Stacker



May 25, 1965 led Dec. 3l, 1962 w. G. DIETRICH 3,185,290

STACKER 5 Sheets-Sheet l May 25, 1965 w. G DIETRICH STACKER 5 Sheets-Sheet 2 Filed Dec. 3l, 1962 .PJMHHNIIIILIIII ilLllllullfllllll il F11--.

May 25, 1965 w. G. DIETRICH STACKER File Dec. 31, 1962 5 Sheets-Sheet 3 May 25, 1965 w. G. DIETRICH 3,185,290

s'rAcKER Filed Dec. 3l, 1962 5 Sheets-Sheet 4 INVENTOR. BY /e/f/z/ ze/w.,

May 25, 1965 w. G. DIETRICH 3,185,290

sTAcKER V Filed Dec. 51, 1962 5 Sheets-Sheet 5 1N VENTOR.

United States Patent O 3,185,290 STACKER Werner G. Dietrich, 336 Central Ave., Wilmette, Ill. Filed Dec. 31, 1962, Ser. No. 248,756 Claims. (Cl. 1598-233) This vinvention relates in general to material handling and more particularly to material stackers. =It deals speciically Iwith an improved mobile material stacker.

Mobile material stackers of the type with which we are concerned are, generally speaking, extremely large pieces of equipment. Conventionally these stackers take the form of a mobile tower structure having a conveyor boom supported from the tower structure by cable rigging including multiple sheaves, winch drive with accessories, housing, etc. The bulk and coniguration of the tower struct-ure tends to make the stacker unwieldy and even dangerous to operate under certain conditions; in -high winds, for example. In addition, these conventional stackers ordinarily utilize individually installed, self-contained drive units to move the stacker, drive the boom conveyor, and rotate, aswell as raise and lower the boom. Accordingly, the amount of normally unused power available is substantial since the power requirements of such a stacker for all facets of normal operation are collectively much lower than the total available power which must be present in component form to supply individual maximum operation demands.

It is an object to provide an 4improved boom-type mobile, material stacker.

It is another object to provide a stacker which is substantially more compact and has a lower center of gravity, with a lower overturning moment, than presently known stackers, facilitating efficient and safe operation in relatively high winds, for example.

It is yet another object to provide a stacker wherein the operator has an unobstructed view of the discharge end of the stacker boom.

It is a further object to provide an improved boomtype, mobile material stacker which utilizes a single pool of power for moving the stacker, rotating the stacker boom, and raising and lowering the boom.

It is still a further 4object to provide a mobile stacker of the `aforedescribed character which utilizes a single prime mover for the aforementioned single pool of power, the pool of power being hydraulic power.

It is yet a further object to provide a mob-ile stacker which incorporates a hydraulic power system constructed and arranged to facilitate a low center of gravity and compact configuration.

It is another object to provide an improved boom-type, mobile stacker of the aforedescribed character in which the hydraulic power system utilizes a power source arrangement having substantially less total horse power than is ordinarily required with stackers -of a broadly similar nature.

it is still another object to provide la stacker of the aforedescribed character employing a substantially simplifie/.i design and construction, and which is easier to maintain than presently known conventional stackers.

The foregoing and other robjects are realized in accordance with the present invention by providing an improved boom-type, mobile material stacker. The invention contemplates a stacker which is entirely hydraulically powered, the hydraulic power being arranged and delivered so as to facilitate a substantially towerless structure having a low center of gravity. This construction permits of completely safe operation in relatively high winds, for example. The stacker is simple in design and construction, making it easy and economical to maintain. Its hydraulic system provides a ready pool of power to move the stacker, drive its boom conveyor, rotate the boom, and lift the boom; all at preset or varying speeds. Neverl@ Patented May 25, 1955 ice ltheless, a relatively low horsepower source of hydraulic power satisfies all the torque requirements of Ithe system.

The invention, both as to its organization and method of oper-ation, taken with `further objects and advantages thereof, will best be understood by reference to the following description taken in connection with the accompanying drawings, in which:

FIGURE 1 lis a diagrammatic view, in side elevation, of a conveying and stacking arrangement including a mobile stacker embodying features of the present invention;

FIGURE 2 is an enlarged elevational view of the mobile stacker illustrating various vertical posit-ions of the stacker boom;

FIGURE 3 `is a plan view of the stacker, illustrating various radial positions of the stacker boom;

FIGURE `4 is a further enlarged side elevational view, in partial section, of a portion of the stacker embodying features of the present invention;

FIGURE 5 is a further enlarged View, partially in section, of the truck construction of the stacker embodying features of the present invention;

FIGURE 6 is an enlarged plan -view of the hydraulic system incorporated in the stacker, illustrating portions of the stacker itself;

FIGURE 7 is a diagrammatric side elevational View, Iwith parts removed, illustr-ating details of the stacker feed hopper and lowering chute construction, and collaterally illustrating a modified form of stacker construction; and

FIGURE 8 is a view taken along line y8 8 of FIGURE 7, with parts removed.

Referring now to the drawings, and particularly to FIGURE l, a mobile material stacker embodying features of the present invention is illustrated generally at 10, in operative relationship with a belt tripper trailer 11 of generally conventional construction. The belt trip-per trailer 1-1 delivers material, which might be coal or iron ore or the like, for example, from a stocking belt 12 to the stacker 10, whereupon the stacker y10, through various manipulations under the direction of an operator, stacks the material in a pile 13 or a number of piles (not shown) bracketing the path of travel of the stacker 10. As will be noted, the stocking belt 1=2 is an endless belt which merely rides up and over the tripper trailer -11 and back into a prescribed endless run, in a well known manner.

The stacker -10 embodying features of the present invention is substantially more compact than its presently known counterparts. It is towerless in the classic sense, as will be noted, and its center of gravity is quite low to the terrain over which it is adapted toV ride. The operators view is unobstructed by any tower structure and safer and more efficient operation of the stacker 10 is assured. The stacker y10 is completely hydraulically operated, utilizing a single, relatively low horsepower prime mover. Utilizing hydraulic power according to the present invention facilitates the low center of gravity and towerless construction.

As has been pointed out, the belt tripper trailer 11 delivers material to the stacker 10 from the stocking belt 12 which continually mns over and through the tripper trailer 11 and dumps the material onto the stacker 10 at a predetermined position. The tripper trailer 11 includes a frame 20 of broadly well known construction mounted on flanged wheels 21 which are adapted to ride on conventional rails 22 bracketing the stocking belt 12. The belt tripper trailer 11 forms no specific part of the present invention; accordingly, it is not described in detail.

Turning to FIGURES 25, the stacker 10 is seen to include a stacker truckframe 30 which rides on the rails 22 mounted on the concrete base 31 forming a trough 32 in which the stocking belt 12 travels in delivering material from a source (not shown) to the `stacker 10 through the medium of the belt tripper trailer 11. A conventional conveyor belt support frame 33 is mounted in the base of the trough 32 and carries appropriately mounted troughing idler assemblies 34 in a well known manner, to support the stocking belt 12. The trough 32 might be several hundred feet long, depending upon the ,application in which the stacker 10 and the tripper trailer 11 are utilized. Y

Though the concrete base 31 has been described in terms of a trough 32, however, it should be pointed out that the trough 32 is not a necessity. The concrete foundation could be placed above the terrain, with adequate cross beam stileners to obtain lateral rigidity and assure parallel longitudinal alignment for the runways of the stacker 10 and trailer 11, for example. Other variations of a base for the rails 22 might also be utilized,

of course. y I I The stacker truckframe 30V supports a turntable 40 for rotation about a vertical axis. The turntable Y40, in turn, pivotally mounts a boom assembly 42 for vertical movement relative thereto, and a control house assembly 43 ixedly mounted on the turntable 40. The power system 44 provides power according to the present invention to; move the stacker truckframe 30 and accordingly the stacker 10 along the rails 22; rotate the turntable 40, and accordingly, the boom assembly 42, arid control house assembly 43 about a vertical axis; raise and lower the boom assembly 42; and [drive a boom conveyor belt 45. K

The stacker truckframe 30 includes a generally rectangular framework 50 from which are dependently mounted four substantially identical dual wheel units 51 adapted to-ride on corresponding rails 22. The stacker 10 is driven along the railsZZ by a combination lluid motor and speed reducer unit 53v according to the present invention, the unit 53 forming a component Vof the power system 44 hereinbefore referred to and hereinafter discussed in detail. The unit 53 is drivingly connected with only the .rear wheel units 51 (see FIGUREAG) through conventional axles 54. A substantially circular track 55 mounted on top of thel framework 50 supports .the turntable 40 fory rotation about the Vertical axis.

The framework 50 of the stacker truckframe 30 is preferably fabricated of longitudinally extending channel members 60 and 61 interconnected by series of trans versely extending wide flange beam sections, 62 in a wellY known manner, such as by welding or the like. A sturdy framework 50 having a generally latticework pattern is defined. The annular rail 55 ,which surmounts the framework 50 is mounted on the longitudinally extending member-s 60 and 61 and the transversely extending beam sections 62 by welding or the like also, as might be expected.

The wheel units 51 are each mounted on a corresponding pair of channel members 61, as best seen in FIGURE 5. Except for the fact that the rear wheel units 51 are driven, while the front wheel units 51' are not, the wheel units 51- are substantially identical in conguration. Accordingly, only one such unit 51 is described in detail here. Corresponding reference numerals are utilized where applicable with the remaining wheel units 51. Before describing the wheel units 51 in detail, however, it should be recognized that the stacker 10 could be provided with a dual drive arrangement. That is, all four wheel units 51 might be power-driven ysince there is no necessity for synchronization between the driven wheels because a hydraulic power system is inherently able to automatically balance itself in direct relation to the demands of required torque.

As best seen in FIGURES and 6, each rear or driven wheel unit 51 is mounted in depending relationship on a corresponding pair of opposed longitudinally extending channel members 61, through the medium of a rigid shaft block 63 welded to the channel member 61 and a bearing shaft 69 extending from both sides of the 4 j block 68. 'Each wheel unit 51 is mounted on a corresponding shaft 69for pivotal movement thereabout on bearing blocks 70 having appropriately formed bearing passages (not shown) extending therethrough for receiving the corresponding ends of the shaft 69 in bearing relationship.

In each wheel unit 51 the bearing blocks 70 are rigidly secured, by welding, for example, to a housing which encloses a pair of double anged wheels 76. The blocks 70 extend between and interconnect a pair of oppositely Vdisposed end plates 77 of the housing 75. In addition, channel members 78 extend between and interconnect the end plates 77, forming sides for the housing 75. The wheels 76 are appropriately mounted on stubv axles 79, journalled through the channel members 7S, as best seen in FIGURE 6.

Up to this point the foregoing is an accurate description of the construction of each of the wheel units 51 on the stacker 10v embodying features of the present invention. The rearwheel units 51 are operatively connected to the drive axles Se. Each of the drive axles 54 is journalled through a corresponding pair of channel members 78 between the wheels 76, and has a driving gear 82 iixed on its outer extremity. The gear 82 meshes with appropriately sizedy transmission gears 83 fixed on the extending ends of the stub axles 779, providing a gear train from the combination uid motor and speed reducer unit 53 to each flanged wheel 76 in a corresponding rear Wheel unit 51.

Since each wheel unit 51 is mounted for longitudinal pivotal movement on a corresponding bearing shaft 69, it will be understood that each wheel unit 51 readily adapts itself to evenly balanced travel on a corresponding rail 22. To accommodate any slight longitudinal movement of a rear driven wheel unit 51 about a corresponding bearing shaft 69 as a result of encountering irregularities in the rails 22, for example, conventional iiexible joints 85 are provided in the axles 54.

As has been pointed out, the turntable 40 is mounted for rotation about a vertical axis on the circular track 55 mounted on top ofthe framework 50 of the stacker truckframe 30. The turntable 40 is rotated by a vanetype torque unit which delines the aforementioned vertical axis in the form of `a Shaft 91 extending vertically Vupwardly through the vane-type. torque unit 90 and forming a part thereof. The vane-type torque unit 90 is broadly conventional in construction and is part and parcel of theV power system 44 hereinbefore referred to. As such, it will be hereinafter discussed in detail.

The aforementioned shaft 91 is xedly seated in a mounting plate assembly similar to a step bearing which is, in turn, welded on top of an opposed pair of channel members 93 in the framework 50 of the stacker truckframe 30. The channel members 93 are preferably welded in back-to-back relationship with corresponding channel members 60 forming components of the framework 50. As will be noted, particularly in FIGURE 5, these backtoback vchannel members 60 and 92 not only ixedly mount the shaft 91 in vertically extending relationship, but also have secured to their lower extremities, by welding or the like, a relatively heavy mounting plate 94 f or the combination fluid motor and speed reducer unit 53. It will be noted that the unit 53 is secured to the mounting plate 94 by conventional machine bolts 95.

The vvane-type torque unit '90 is integrated into the framework of the platform 40. The framework 100 includes a pair of centrally disposed, horizontally displaced plates 101 interconnected by a rectangular inner channel frame 102 through welding or the like. Conventional frame members, including transversely extending channel members 103, interconnect the Vplates 101 and the channel frames 102 with an outer pair of channel frames 105, preferably arranged octagonally in plan. The outer pair of channel frames 105 mount a series of roller units -106 between them, spaced at intervals of about the octagon which the frames 105 define, to overlie the track 55. The roller units 106 include conventional unflanged rollers 107 journalied on bearing shafts 163 mounted between the channel frames 105.

Seated on the platform 160 and secured thereto is the power pool and prime mover arrangement 110 of the power system 44. The arrangement 110 generally comprises a single drive motor 112, fluid pumps 113 and 114, and a hydraulic fluid reservoir 115, with suitable accessories including filters and the like. A walk-in housing 116 (see FIGURE 1) is preferably constructed over the arrangement 110. The construction and operation of the arrangement 111i is hereinafter discussed in detail collateral to a discussion of the entire power system 44.

In addition to driving the stacker truckframe 30 along the rails 22 and rotating the platform 40 on the truckframe 36 about a vertical axis, the power system 44 raises and lowers the stacker boom assembly 42 accordingly to the present invention, as has hereinbefore been pointed out. This raising and lowering of the boom assembly 42 amounts to vertical pivotal movement of the stacker boom assembly and is effected by a pair of generally vertically disposed fluid rams 12%) pivotally mounted on the framework 100 of the platform 4@ through pivot brackets 121, and appropriately connected with the boom assembly 42. Since the fluid rams 120 form components of the power system 44, in a manner broadly similar to other components hereinbefore referred to, their construction and operation will also hereinafter be discussed in detail.

The stacker boom assembly 42 includes a boom 122 of substantial length (nearly three times the length of the supporting truckframe 30, for example) pivotally mounted on an anchor housing 123 of heavy construction. The housing 123 forms a solid base for vertical movement of the boom 122 about its horizontal pivot axis 124. The anchor housing 123 is preferably formed of steel plates welded together around an appropriate framework (not shown) rigidly secured to the framework 160 of the platform 40. The anchor housing 123 is appropriately shaped to receive a prescribed amount of ballast for counterbalancing the boom 122. In this instance, the ballast comprises steel punchings or tbe like in a concrete mortar base, but it should be understood, of course, that other ballast material might be utilized.

The boom 122 includes a shaft bearing foot end section 13b and a skeletal outer section 131 interconnected at a reinforced girth box frame 132 to which the fluid rams 1213 are operatively connected. The conveyor belt 45 is mounted on and extends between the sections 13G and 131, as best seen in FIGURE 2.

The foot end section 13G of the boom 122 is conventionally constructed of framing members 133 joined by welding or the like. Side panel members 135 and a bottom panel member 136 formed of steel plates are appropriately welded to the interconnected framing members 133 adjacent the free end of the foot section 131i. A spaced pair of bearing collars 149 are mounted on the foot end section 13? at its free end for receiving a bearing shaft 141 xed to the anchor housing 123. The shaft 141 pivots in opposed flange-type bearings 142 secured to the anchor housing 123.

The skeletal outer section 131 of the boom 122 comprises four longitudinally extending stringers or cords 145 comprised of light weight, high strength structural steel or the like. The longitudinally extending stringers 145 are interconnected by longitudinally spaced cord stiffeners 146 and laterally extending top bracings 147, each fabricated in substantially the same manner as the longitudinal stringers 145. The longitudinal stringers 145 are, of course, rigidly secured to the foot end section 131 and to the box frame 132 by welding or the like.

The box frame 132 is preferably fabricated of structural steel, heavily reinforced against any deformation due to concentrated loads at the points of connection with the hydraulic rams 120. These points of connection are defined by laterally extending, reinforced pivot pins 132:1 to which corresponding fluid rams are appropriately connected.

To provide the boom 122 with longitudinal stiffness and counteract any tendency for the boom to slew or bend when it is being rotated at a high rate of speed, for example, or is operating in a high wind, lbracing cables 1143 are secured at opposite ends of the boom and braced outwardly along the length thereof by struts 14? (see FIG- URE 3).

Referring for a moment to FIGURES 7 and 8, a modified boom bracing arrangement 14851 is illustrated. Such an arrangement might be provided to militate against special operating `conditions of the stacker A141, such as lateral wind forces of substantially high velocity or, on the other hand, an exceedingly fast turntable rotation. The arrangement 1-48a features rollers lb, either singly or in pairs, which are mounted on wing members 148e formed on opposite sides of the box frame 132. The rollers 148]) rotate in the plane of the box frame and are adapted to ride in opposed guide tracks 148d which are curved to follow Ithe curved path which the box frame 132 follows as the boom 122 is raised and lowered. The guide tracks 148d are rigidly secured to the housing assembly 43 mounted on .the turntable 40 and are reinforced against lateral deflection so as to counteract lateral deflection of the boom 122 and, in addition, reduce the side thrust on the boom pivot bearings 142. The foregoing arrangement 148:1 might be provided in lieu of or in addition to the stilening tables `148 immediately hereinbefore discussed, to provide stability against lateral slewing motions of the boom 122.

The conveyor belt 45, which is mounted for endless travel on the boom 122, as has been pointed out, is trained around a drive pulley 150 mounted in a conventional manner adjacent the discharge end of the skeletal boom section 131, and a foot pulley 151 having conventional take-up bearings (not shown) associated therewith mounted in a conventional fashion on the foot end section 139 of the boom 122. The Conveyor belt 45 is supported along its carrying strand by conventional troughing idler assemblies 152 mounted on the boom 122, and on its -return strand by conventional return idler assemblies 153, both mounted on the boom 122 in any well known manner. A snub pulley 154 is adjustably mounted adjacent the drive pulley 15) to adjust tension on the belt 45. Since the construction and arrangement of the drive pulley, the foot pulley i151, the idler assembly 152 and i153, and the snub pulley 154, is broadly conventional, they are not shown in any substantial detail.

The drive pulley 1511 is rotated so as to drive the conveyor belt 45 Iby a uid motor 16) mounted on the discharge end of the skeletal section 131 of the boom 122. The liu-id motor 151D is operatively connected to the drive pulley 150 through a conventional speed reducer 161 and a drive shaft 162. The motor 16d forms a component of the power system 44 hereinbefore referred to and hereinafter discussed in detail.

Also mounted on the platform 40, as has been pointed out, is the control house assembly 43. The control house assembly 43 includes a structural steel A-frame 165 which supports an operators cab 166 immediately over the boom 122. The A-frarne straddles the boom 122 and the anchor housing 123, as will be recognized, and is high enough that the boom 122 is permitted its full range vertical movement (about 18 upwardly from the horizontal).

The A-frame 'll' includes a generally vertically extending front column 169 of buttress-type construction interconnected with inclined rear stringers 170 by horizontal bracings 171 and diagonal stilfeners 172, preferably fabricated of the same material. The lowermost ends of the buttressed front columns 169 and the inclined str-ingers 170 are rigidly secured to the platform 40 in any conventional manner, such as by welding or the like.

VVV7 The operators cab 166 includes a platform 175 mounted on the uppermost extremity of the A-frame 165. The platform 175 supports the walls 176 and roof 177 on a Vsimple framed housing structure for protecting the operator from the elements. The sides 176 and roof 177 of `the cab 166 are preferably sheet metal or the like, and windows 178 are provided in frame openings set in the sides. A pulpit-type control panel 179 from which the power system 44 is manipulated by the operator according to the present invention, is appropriately mounted in the cab 166.

To direct the material being delivered from the stocking belt (via tripper trailer 11) onto the charging end of the top strand of the conveyor belt 45, a surge hopper 185 is provided mounted on the uppermost of the inclined stringers 170 of the A-frame 165, while a material lowering chute l186 is rigidly connected to the foot end section 131 of the boom 122. Accordingly, as would be expected, the surge hopper 185 is vertically fixed while the material lowering chute 186 moves vertically with the movement of the boom 122. Referring to FIGURE 7, the construction and operation of the hopper 185 and lowering chute 186 are shown in some detail.

The surge hopper 185 will be seen to comprise a generally box-like structure formed of steel plate, open at its front end 188 and along its bottom 189 forward of an inclined impact plate 190 forming a portion of the bottom of the surge hopper 135. Material is delivered from the stocking belt 12 (off of the tripper trailer 11) onto the inclined plate 190 where `its falling speed is broken. The material then falls off the inclined plate 190 in the manner illustrated, into the material lowering chute 186.

The material lowering chute 186 is also generally boxlike in construction, has an open forward end 192, and is open along its bottom 193 forward of an inclined plate y194 forming a portion of the bottom v193. A second 1nclined plate 1-9'5 forms a shelf in the lowering chute 186 above the inclined plate 194. It will thus be seen that the material falling from the surge hopper 185 first encounters the inclined plate 195 which again breaks its falling speed, whereupon the material falls downwardly onto the lower inclined plate 194, once more breaking 'its falling speed. The material then departs the material lowering chute 186 onto the charging end of the top strand of the conveyor belt 45 without damaging impact effect upon the belt 45.

As illustrated in FIGURE 7, regardless of the vertical position of the boom 122 the material delivered from the stocking `belt 12 to the stacker belt 45 strikes the belt with minimum impact since the combination surge hopper 185 and lowering chute 186 cooperate in the foregoing manner in all such positions. This concept in material handling is referred to as stone box lowering of materlal, providing a substantially impact-free lowering thereof.

As has been pointed out, the power system 44 which manipulates the stacker according to the present invention includes a combination motor and speed reducer unit 53 which drives the stacker 10 along the rails 22, a vane-type torque unit 90 which is effective to rotate the platform 40 on the stacker truckframe 30, two fluid rams 120 which are effective to raise and lower the boom 122, and a fluid motor 160 which drives the stacker conveyor belt 45. The power system 44 further includes vthe iiuid pumps 113 and 114 which supply fluid under pressure to the immediately aforedescribed components of the power system 44, as well as a conventional electric motor 112 which drives the pumps 113 and 114. The operation in the cab 166 controls the flow of uid from the pumps 113 and 114 to appropriate components of the power system 44 to drive the stacker 10 along the tracks 22, rotate the platform 40 so as to swing the boom 122 laterally of the tracks 22, raise and lower the boom 122 and drive the conveyor belt 45, as has been pointed out. The fluid pumps 113 and 114 are directly connected through internal conduits (not shown) -to the hydraulic uid reservoir 115 from which they draw hydraulic fluid on demand.

The fluid pump 114 serves as a single pool of power for the combination motor and speed reducer unit 53, the vane-type torque unit 90, and the fluid rams 120. The uid motor 160 which drives the conveyor belt 45 is driven on the other hand, by the fluid pump 113. Each of the pumps 113 and 114 is driven by the prime mover electric motor 112, a motor of relatively low horsepower,

through a corresponding end of its double end output shaft 200.

The combination motor and speed reducer unit 53 which drives the stacker 10 along the rails 22 is a broadly conventional fluid motor which utilizes fluid under pressure to turn the axles 54 in a well known manner at a predetermined speed. The details of construction of the unit 53 form no part of the present invention, and consequently, they are not set out herein. Suice it to say that fluid under pressure is directed from the pump 114 through a fluid conduit arrangement 201 to the unit 53 to turn the axle 54 at a predetermined rate to drive the stacker truck 30 along the rails 22. The fluid returns in a well known manner through the conduit arrangement 201 to the reservoir 115. The rate of ow of fluid under pressure to the unit 53 from the pump 114 is controlled yby the operator from the console 179 in the cab 166 through conventional electrical circuitry 202 and a solenoid operated valve 203 in the uid conduit arrangement 201. As will be noted, the fiuid conduit arrangement 201 passes downwardly through a bore 204 in the shaft 91 of the vane-type torque unit to reach the unit 53.

The platform 40 and consequently the boom 122 are rotated about the axis defined by the shaft 91 of the vanetype torque unit 90 as has been pointed out. The torque uni-t 90 is preferably a conventional hydraulic torque actuator of the rotating vane-type construction. An example of such an actuator is the Rotac model S manufactured by the Ex-Cell-O Corporation of Greenville, Ohio. In general, the actuator 90 includes a vane 210 fixed to the shaft 91. A housing 211 encloses the vane 210 and the central portion of the shaft 91 and is fixed in the turntable framework 100. The housing 211 carries an inwardly extending fixed vane 212. By directing fluid under pressure to opposite sides of the vane 212, it will be understood that the housing 211 and consequently the turntable 40 will be forced to turn about the axis defined by the fixed shaft 91.

With the stacker 10 constructed according to the present invention, the maximum turning angle required is 180, since the stacker boom 122 need only move its discharge end from the farthest laterally extending point on one side of the truck frame 30 to the farthest laterally extending point on the other side thereof during the operation of the stacker. The vane-type torque unit 90 readily facilitates this 180 movement, being of the single fixed vane construction.

In a manner broadly similar to the manner in which fluid is directed from the pump 114 to the fluid motor and speed reducing unit 53, fluid is directed from the pump 114 to the vane-type torque unit 90 through a fluid conduit arrangement 216 (see FIGURES 4 and 6). The operator controls the rate and directional ow of iiuidV under pressure in the conduit arrangement 216 through the medium of a solenoid valve arrangement 217 in the fluid conduit arrangement 216. The solenoid valve arrangement 217 is electrically operated through the circuitry system 202 hereinbefore discussed, from the console 179 in the control cab 166.

The single pool of power embodied in the pump 114 also provides fluid under pressure to raise and lower the boom 122 through the medium of the fluid rams 120 from the pump 114 through a duid conduit arrangement 225. A conventional solenoid valve 226 in the fluid conduit arrangement 2251controls the ow of fluid under pressure to and from the fluid rams to position the boom 122 in any prescribed vertical position within its range of travel. The solenoid operated valve 226 is controlled electrically through the aforementioned circuitry system 262 from the console 179 in a Well known manner.

While the huid pump 114 provides iluid under pressure to alternatively or collectively drive the stacker along the rails 22, rotate the turntable 40 about its axis, and raise or lower the boom 122 in the foregoing manner, the pump 113 is effective to direct uid to the duid motor 160 through the iluid conduit arrangement 230 to drive the conveyor belt 45. The motor 160 is separately driven by a single pump, the pump 113, because a constant belt speed must normally be maintained. In this light, the conveyor belt 45 is ordinarily driven somewhat faster than the stocking belt 12 to assure that material does not pile up on the belt 45.

The ow of iiuid under pressure from the pump 113 to the `duid motor 161i is regulated through the medium of a conventional solenoid operated valve 231 in the fluid conduit arrangement 230. The solenoid operated valve 231 is manipulated from the console 179 in the cab 166 by the operator who appropriately controls the electrical system 202 hereinbefore discussed.

The pump 113 is preferably a constant delivery vanetype pump, while the pump 114 is preferably a variable delivery pressure compensated piston pump of well known construction. These pumps 113 and 114 are driven in a conventional manner by the motor 112 which is a relatively low horsepower electric motor of high torque, high slip characteristics. The power system 44 incorporating the pumps 113 and 114 in the electric motor 112 eliminates any idle hooked up horsepower, since each driving component of the system 44 (the vane-type torque actuator 99, for example) draws power from its source (pump 114) only to the extent which it requires power.

The system 44 permits variable speed operations without an elaborate electrical control system. The flexibility of power distribution is best expressed by the fact that individual demand of torque loads `for the individual drives -are taken from the pool `of ready power, produced constantly by a pump with the built-in feature of nonstalling during any of the operations. This, when compared with individual electric motor drives for each of the driving operations of a stacker, has an even greater advantage due to the fact electric motors when subjected to heavy overloads will inally drop 4out and become stalled. In contrast, `any overload in the present system is absorbed by the power pool and excessive demand will simply slow down the time element of lthe individual performance cycles in proportion to the unused reserve stored in the power pool.

To best illustrate the oper-ation of thestacker 10 embodying features of the present invention, let us hypo- Ithetically consider that the pump 114, which is utilized for operating the stacker drive unit 53, the turntable rotating torque actuator 99, and the boom adjustment fluid rams 120, requires a torque demand equal to 75% .of the total power -available from the pump 114 to propel the stacker at 80 fpm, (feet per minute). The balance of power available from the pump 114, 25% thereof, will be sufficient to rotate the turntable 40 at a speed of 2% minutes for passing through Aits maximum arc of 180 with a top speed of 95 fpm. This would then exclude raising the boom proper. Should the latter oper-ation be required, the 80 fpm. rate of stacker travel could be reduced to satisfy the boom raising demand. After all, the 80 fpm. requirement `is solely a requirement for fast travel of the stacker and most stackers travel at 30 to 40 fpm. Then too, the power of the electric motor 112 is not fully applied since the boom conveyor belt 45 would not be running with the stacker travelling at 80 fpm.

A discussion of an exemplary practical operation cycle of the stacker 10 will bring the various power demands into clearer focus. For example, to begin with the stacker is at rest with the -boom 122 in its lowest, out of service, position. The operator might choose to lstart the stacker 10 to drive, propelling the stacker 10 at 80 fpm.

to reach a distance location. He might also wishto move the boom 122 iirSt, and afterwards start the stacker 10 drive or induce both operations concurrently. The vertical travel of the boom 122 is based on a three to four minute time cycle. The pump 114 has enough capacity to satisfy -t-his torque demand; therefore, both operations can be started. At the very moment of such a start, the demand -for overcoming the inertia of the stacker to get it under way, ie., in the time of the greatest demand on the pump 114, the upward motion of the boom 122 (during this high demand) might be slowed -t-o less than its designated time cycle of three to four minutes. This results in a slowdown of perceivable short duration. However, as soon as the stacker 10 is rolling the power demand for .its drive drops and the uid rams 120 take over full power operation.

With the stacker 10 at the desired location, the turntable torque actuator 90 might be called into service, and since the torque demand for rotating the boom 122 is low, the pump 114 at this time will have enough reserve capacity for any `full power boom 122 adjustment, should Ithis be necessary. Inasmuch as the separate pump 113 is provided for the boom conveyor drive moto-r 160, it can Ibe started concurrently with these operations.

The next Itorque demand most likely would be shifting the stacker, either for filling a limited gap in the storage pile or for a continuous pile-windrow operation over a large area. Whatever the case might be, the spot shifting or continuous movement can be had at any selected speed since no other torque demands at that time are made on the pump 114. Should a boom 122 adjustment become necessary it can be easily taken care of during this operation cycle with the stacker 10 running at a normally low speed, at which time the demand upon the pump 114 is lower. Should lowering of the boom 122 be required, this is done merely by lay-passing oil inasmuch as no torque demand Vis required.

To more eiectively illustrate the manner in which various power functions of the stacker 10 can be manipulated as much as desired while using a relatively low horsepower prime mover, a performance schedule `for'these hydraulic operations is set out below. In this case the electric motor 1'12 is of a substantially Ilow horsepower classification, preferably 60 horsepower. Yet it can provide all horsepower requirements of the stacker 10 under all practical conditions of operation (the designation gpm. means gallons per minute in the performance schedule set out below) Performance schedule for hydraulic operations of stacker [Unit performance: Separate requirement] 60 HP. electric motor 1200 rpm. high torque 5 to 8% slip will develop from 27 5 to 325 starting Iand surge torque.

Combinations of operations, simultaneously H.P. (a) Run stacker fpm. and raise boom 54 (b) Rotate turntable, raise boom and run boom conveyor 56.5

(c) Run stacker 6 fpm., raise boom, run conveyor and rotate turntable 58.3 (d) Run stacker l0 fpm., raise boom, run conveyor 57-.0 (e) Run stacker 30 fpm., run conveyor, rotate turntable 54.0

lead 2 92.5

1 Torque surge of 60 H.P. will not stall these operations. It may causes temporary slow down, until starting of stacker drive is overcome.

1. N ot. recommended, nor practical.

It will be recognized that a new and improved stacker has been illustrated which is simple and yet sophisticated in construction and operation. Its hydraulic power system 44 is uniquely adapted to performing all the power functions of the 4stacker 10 according to the present invention while permitting of a stacker construction which is compact and has a relatively low center of gravity. Accordingly, safe operation is possible in high winds, for example.

Because of the unique arrangement of the superstructure and the power system 44, a stacker 10 is provided with a lesser amount of mechanical equipment than has heretofore been required. For example, either the conventional ring gear requiring pinionengagement or a chain and sprocket drive or the like, commonly referred to as bull wheel rigs, utilized for rotation of the turntable platform, are eliminated. The stacker 10 is accordingly simpler in construction than known stackers of a broadly similar nature, making it relatively easy and economical to construct and maintain. Furthermore, the operator, from a relatively low vantage point, has an unobstructed view of discharge end of the boom 122 and can unerringly deposit material wherever he chooses.

The power system 44 of the stacker 10 provides a ready pool of power to effectively move the stacker, drive its boom conveyor, rotate the boom, and lift the boom at prescribed speeds. Nevertheless, a relatively low horsepower (60 H.P., for example) prime mover provides the basic power source for torque requirements of the stacker 10.

While several embodiments described herein .are at present considered to be preferred, it will be understood that various improvements and modifications may be made therein, and it is intended to cover in the appended claims all such variations and modifications as may fall within the true spirit and scope of the invention.

What is desired to be claimed and secured by Letters Patent of the United States is:

1. A mobile material stacker having a compact configuration and a low center of gravity, comprising: movable truck means, uid motor means on said movable truck means for moving said truck means, platform means mounted on said truck means for rotation about a vertical axis, fiuid motor means between said platform means and said truck means for rotating said truck means, a boom assembly pivotally mounted on one side of and extending across said platform means for vertical movement relative to said platform means, fluid motor means mounted on the opposite side of said platform means from said one side and operatively connected to said boom asassembly to raise and lower said boom assembly, a-

conveyor belt mounted on said boom assembly for endless movement thereon, fluid motor means mounted on said boom assembly for moving said conveyor belt, upstanding frameworky means mounted on said platform means, bracing means mounted on said framework means for operative engagement with said boom assembly to laterally stabilize said boom assembly as it is raised and lowered, a first fluid pump mounted on said truck means for providing fluid under pressure to said fluid motor means for moving saidconveyor belt, a second fluid pump on said truck means for providing fluid under pressure to the remaining fluid motor means, and a prime mover mounted on said truck means for driving both of said fluid pumps, said prime mover having a substantially lower horsepower rating than the total horsepower required to simultaneously operate each of said fluid motor means at maximum practical operating speed.

2. The stacker of claim 1 further characterized in that said bracing means includes arcuate track means mounted on said platform means and roller means carried by a boom assembly for travel in said arcuate track means.

3. The mobile stacker of claim 1 further characterized by and including a material receiving hopper fixed on said framework means and a cooperating material lowering chute fixed on said boom assembly for vertical movement therewith and cooperation with said hopper means in lowering material onto said conveyor belt.

4. A mobile material stacker having a compact .configuration and a low center of gravity, comprising: movable truck means, fluid motor means on said truck means for moving said truck means at speeds up to a maximum practical operating rate, platform means mounted on said truck means for rotation about a vertical axis, fluid motor means between said platform means and said truck means for rotating said platform means at speeds up to a maximum practical operating rate, a boom assembly pivotally mounted adjacent one side of and extending across said platform means for vertical movement relative to said platform means, fluid motor means on the opposite side of said platform means for raising said boom assembly at speeds up to a maximum practical operating rate, said boom assembly carrying a conveyor belt for endless movement on said assembly, fluid motor means on said boom assembly for driving said conveyor belt at speeds up to a maximum practical operating rate, fluid pump means on said'stacker for supplying fluid under pressure to each of said fluid motor means, said pump means comprising a first fluid pump and a second fiuid pump, said first fluid pump supplying fluid under pressure to the fluid motor means for driving said conveyor belt, and said second fluid pump supplying fluid under pressure to the remaining :duid motor means, and a prime mover on said stacker for driving said pumps, said prime mover having a substantially lower horsepower rating than the total horsepower required to simultaneously operate each of said fluid motors at maximum practical operating rates.

5. The 'stacker of claim 4 further characterized in that said fluid motor means for rotating said platform means includes a vane-type torque actuator interconnected between said platform means and said movable truck means, energization of said vane-type torque actuator being effective to rotate said platform means relative to said movable truck means in a predetermined direction and at a predetermined turning rate up to a maximum practical operating rate.

References Cited by the Examiner UNITED STATES PATENTS 1,311,298 7/19 Stuart 214-10 2,572,029 10/51 Huston 212-38 2,781,890 2/57 Mercier 198-36 2,911,111 11/59 Grove 212-35 SAMUEL F. COLEMAN, Primary Examiner.

WILLIAM B. LA BORDE, Examiner. 

1. A MOBILE MATERIAL STACKER HAVING A COMPACT CONFIGURATION AND A LOW CENTER OF GRAVITY, COMPRISING: MOVABLE TRUCK MEANS, FLUID MOTOR MEANS ON SAID MOVABLE TRUCK MEANS FOR MOVING SAID TRUCK MEANS, PLATFORM MEANS MOUNTED ON SAID TRUCK MEANS FOR ROTATION ABOUT A VERTICAL AXIS, FLUID MOTOR MEANS BETWEEN SAID PLATFORM MEANS AND SAID TRUCK MEANS FOR ROTATING SAID TRUCK MEANS, A BOOM ASSEMBLY PIVOTALLY MOUNTED ON ONE SIDE OF AND EXTENDING ACROSS SAID PLATFORM MEANS FOR VERTICAL MOVEMENT RELATIVE TO SAID PLATFORM MEANS, FLUID MOTOR MEANS MOUNTED ON THE OPPOSITE SIDE OF SAID PLATFORM MEANS FROM SAID ONE SIDE AND OPERATIVELY CONNECTED TO SAID BOOM ASSEMBLY TO RAISE AND LOWER SAID BOOM ASSEMBLY, A CONVEYOR BELT MOUNTED ON SAID BOOM ASSEMBLY FOR ENDLESS MOVEMENT THEREON, FLUID MOTOR MEANS MOUNTED ON SAID BOOM ASSEMBLY FOR MOVING SAID CONVEYOR BELT, UPSTANDING FRAMEWORK MEANS MOUNTED ON SAID PLATFORM MEANS, BRACING MEANS MOUNTED ON SAID FRAMEWORK MEANS FOR OPERATIVE ENGAGEMENT WITH SAID BOOM ASSEMBLY TO LATERALLY STABILIZE SAID BOOM ASSEMBLY AS IT IS RAISED AND LOWERED, A FIRST FLUID PUMP MOUNTED ON SAID TRUCK MEANS FOR PROVIDING FLUID UNDER PRESSURE TO SAID FLUID MOTOR MEANS FOR MOVING SAID CONVEYOR BELT, A SECOND FLUID PUMP ON SAID TRUCK MEANS FOR PROVIDING FLUID UNDER PRESSURE TO THE REMAINING FLUID MOTOR MEANS, AND A PRIME MOVER MOUNTED ON SAID TRUCK MEANS FOR DRIVING BOTH OF SAID FLUID PUMPS, SAID PRIME MOVER HAVING A SUBSTANTIALLY LOWER HORSEPOWER RATING THAN THE TOTAL HORSEPOWER REQUIRED TO SIMULTANEOUSLY OPERATE EACH OF SAID FLUID MOTOR MEANS AT MAXIMUM PRACTICAL OPERATING SPEED. 